Flying shear



April 7, 1942. D. A. JOHNSTON FLYING SHEAR Filed April 2l, 1959 8 Sheets-Sheet l `April, 7, 1942. D. A. JOHNSTON FLYINGV SHEAR 8 Sheets-Sheet 2 Filed April 2l,A 1939 April 7, 1942- D. A. JOHNSTON FLYING` SHEAR Fi Led April 21, 1939 8 Sheets-Sheet 5 m" Ilma- B E I April 7, 1942. D. A. JOHNSTON 2,278,786

FLYING'- SHEAR Filed April 21, 1959 8 Sheets-Sheet 4 AME 7, E94. D. A.'JoHNsToN FLYING SHEAR Filed April 2l, 1939` 8 Sheets--SheefI 7 D. A. JOHNSTON FLY ING S HEAR Filed April 2l, 1959 8 Sheets-Sheet 8 Patented Apr. `7, 1942 UNITED STATES PATENT OFFICE 20 Claims.

This invention relates generally to a machine for shearing of! lengths of stock and more particularly to an automatic machine for shearing ofi predetermined lengths of formed metallic sections of stock of such sections as the stock issues from a forming machine or other apparatus utilized in the production or iinishing of the same. The invention also relates to various mechanical devices and arrangements the use of which in the combinations to be hereinafter stated enables a machine for the purpose stated to have certain desirable operating characteristics which will be later set out.

Heretofore, in machines for the purpose described dimculty has been encountered in synchronizing the movement ofthe cutting mechanism with the movement of the stock as it issues from the production line and thev diiiiculty is especially aggravated in the case of highstock speeds where the requirements are that the stock be sheared into relatively small lengths having a reasonable degree of uniformity in length. The cutting of the rapidly moving stock into short lengths necessarily requires a high rate of reciprocation of the structure immediately supporting the cutting dies or other tools and, by reason of the fact that in the devices heretofore employed for the purpose the parts making up the reciprocating parts were of substantial mass and weight, the operation of the devices was attended by excessive vibration of the machine as a whole resulting in rapid wear and loosening of the automatic cut-oil. This feature is of importance where the cut-on machine is used in conjunction with a high speed continuous or semi-continuous production line as it enables the cut-oil machine to be coupled closely to the production apparatus and prevents variations in the lengths of the pieces being cut oil and minimizes danger of parts and frequent break downs of the machines.

A further object of the invention is the provisionin a machine of the type described of an arrangement whereby the rate of travel of the stock cutting implements may be synchronized with the rate of travel of the stock'through a forming machine or other production or. finishing apparatus in such manner that variations in thej` speed of operation of such formingmachineforesu other apparatusrwillbe reflected by-corresp0nd ff lngvariations in the speed of operation-of the 5c injury to the cutting mechanism.

Another object of the invention is the provision in a machine for the purpose described of an arrangement whereby the rate of travel of vthe cutting implements along the path of travel of the stock being cut may be very readily and minutely adjusted by the simple manipulation of a readily accessible controlling element. In the operation of automatic cut-oi machines where relatively high stock speeds are encountered, it is impractical to rely on any mechanical contact between the stock and the cutting implements or the carriage immediately supporting such implements to effect synchronism between the stock and implements and it has, therefore, been proposed to provide a quick acting power -means to initiate and maintain movement of the carriage supporting the cutting implements and to provide a lightly actuated trip for the purpose of instigating actuation of the power means. In arrangements of this character the length of stock being sheared is necessarily determined by the position of the trip lever, the rate of movement of the stock, and the time interval between the instigation of actuation of the power means and the moment of contact between the cutting implements and the stock and it should thereforebe apparent that for satisfactory operation of machines of this character such intervals of time must be constant for each successive cycle of operation. andv that in additionthe rate of travel of the cutting implement as they encounter the stack must be capable of precise adjustment. By the use of certain instrumentalities to be hereinafter fully described such characteristics are attainable.

Yet another object of the invention is the provision in a machine of the type utilizing a shear or cutting dies movable along with the stock being cut of an arrangement whereby the stresses imposed on the shear elements or dies and their immediate supporting and operating elements are proportional to the shearing and cutting resistances of the stock being cut. In the case of stock having the same physical characteristics, the

.stresses imposed are proportional to the crosssectional area of the stock and, in either event, the imposition of lighter loads in the cutting of thinner or softer stock results in a material prolonging of the life of the machine since unnecessary stresses and forces are obviated.

A still further object of the invention is the provision of an improved arrangement for slidably mounting the die carriage which reciprocates back and forth and, during the time of actual cutting, moves in synchronism with the continuously moving stock. The purpose of the improved mounting means is to afford a more accurate and uniform alignment of the carriage with the path of travel of the stock and various operating mechanisms associated with the carriage in the machine. It is also my intent that improved means be provided to reciprocate the carriage whereby a cushioning action at the end of each stock of the carriage be inherently effected by the action of the carriage reciprocating means in order that shock and vibration due to impact may be reduced to a minimum.

I also propose to provide an improved arrangement for the cyclic movement of the shearing dies on the reciprocating carriage which will result in the optimum distribution of power and the optimum variation in the rate of movement of the shearing dies throughout each cycle. With the cutting implement in outer inoperative position alarge force is exerted to initiate movement of the same toward the stock, 'the force resulting in progressive acceleration from the starting position, an average uniform rate of travel during the cutting operation, and a decreasing rate of travel to the inward limit of its stroke. The completion of the cycle, i. e., the return of the die to its outer inoperative position, is accomplished in the same manner but, due to the fact that no cutting takes place, no stresses, other than that required to vmove the die, is set up in any of the parts.

It is a more general object of the invention to provide an improved apparatus for moving and controlling the movement of a reciprocating carriage and of a member cyclically movable on such carriage. 'I'he general purpose is to enable suiilcient operative power to be applied to an ele- Y ment whose movement is required to be so compounded and to control such means in such manner that more complete adjustments may be effected, less input power required, smoother operation eiected, ruggedness enhanced, and required maintenance substantially reduced.

Included among the advantages sought to be attained by the apparatus of this invention are the prolonging of the life of the shearing means employed, the insurance of the accuracy as to length of the pieces being severed and a compact design of the machine capable of utilizing the principles of the invention. These and other objects and advantages of the invention will become apparent from a consideration of the accompanying drawings and the following detailed specification wherein there is specifically disclosed an automatic cut-off machine utilizing the principles of the invention. It should be understood, of course, that the machine disclosed rep- .resents but a, preferred embodiment of the invention as obviously many novel principles incorporated herein are applicable to a Wide variety of uses.

In the drawings:

Figure 1 is aside elevation, partly in section, of an automatic cut-off machine;

Figure 2 is a plan view of a portion of the machine of Figure 1;

Figure 3l is an end elevation, partly in section, of the machine of Figure 1;

Figure 4 is a cross-section of the machine taken along the line 4--4 of Figure 3;

Figure 5 is a cross-section of the machine taken along the line 5 5 of Figure 1;

Figure 6 is a cross-sectional detailed view illustrating the manner of slidably mounting the oscillating carriage;

Figure 7 is a sectional view'taken along the line 1 1 of Figure 1;

Figure 8 is a cross-section of the machine of Figure 1 taken along the line 8 8;

Figure 9 is an elevation of the instrumentalities employed to control the reciprocation of the carrlage;

Figure 10 is an end view of the apparatus of Figure 9;

- Figure* 11 is a schematic diagram'of a syn- `chronizing arrangement utilized in the machine of Figure 1;

Figure 12 is a fragmentary sectional plan view of the machine of Figure 1 illustrating a modified driving arrangement; and

Figure 13 is a sectional view of the valve of Figures 9 and 10.

Referring now to the drawings andI more particularly to Figures 1 to 4 thereof, the machine representing the preferred embodiment of the g l structed to afford passage of continuously moving stock, indicated by reference numeral I3, as the latter issues from a forming mill or other production machine with which the instant machine may be used inoperative relation with the carriage, and includes driving means for the carriage which is of such character that the carriage may be moved along with the stock-reaching a synchronous speed with the stock during a ,portionl of its travel. 'I'he means employed to reciprocate the tool slide is operative to move the shearing or other tool employed into engagement with the moving stock and to effect its intended function within the stated portion of travel of the carriage.

Base I0 is provided along its upper wall with a plurality of spaced pairs of parallel hardened steel rails I4 which are removably secured to suitable recesses provided in the upper wall of the base and whose upper and inwardly directed surfaces are carefully aligned and machined to provide an accurate path for the reciprocating movement of the carriage. Engaging the rails I4 on their upper faces are the outer races of bearings I5 carried on stepped sections of horizontal spindles I6 carried in 'turn by downwardly extending projections I'I of the carriage II. See

Figure 6. To prevent upward movement of the carriage relative to the base during operation A of the machine, outward extensions of the spindles I6 have secured thereto anti-friction bearings I8 the outer races of which move un.

derneath hardened steel strips I9 carried by the Z bars 20 suitably fastened to the upper wall of the machine base I0. To provide means to maintain the lateral alignment of the carriage II as the same reciprocates back and forth, each of the projections I1 carries vertically' positioned spindles 2| which extend below the projections to mount anti-friction bearings 22 the outer races of which move along the inner vertical surfaces of the rails I4. The carriage and base is provided with four assemblies as shown in Figure 6-one at substantially each of the corners of the carriage. It should be apparent that the above described construction provides an improved arrangement for the anti-friction sliding support of the reciprocating carriage on the base. The

hardness and quality of races and rolling elements of the bearings, together with similar characteristics of the rails 4 and strips I9, results in very accurate guidance and long life. Also the maintenance of the. sliding support is simplied since the bearings, rails and strips are readily replaceable.

Carriage is slidably moved' on the support described above by a piston 24 housed within cylinder 25 (Figure 4) and connected with an integral downwardly extending projection 26 of the carriage by means of the piston rod 21. A pivot pin 26 connects the rod 21 with the projection 26 to -allow for slight variations in the alignment of the parts. Fluid under pressure is supplied to either end of the cylinder 25 by a iluid pump 30 located in a bath 26 of hydraulic uid in the lower portion of the base I0. 'I'he outlet of fluid pump 36 is connected with a fourway valve, indicated generally at 3|, (se'e Figures 8 and 9) by means of -a conduit 32 and the valve in turn is connected with the iront and rear ends of the cylinder 25 by the conduits 33 and 34, respectively.

Pump 3|) is a variable displacement pump, preferably of the "Vickers type and, as is well understood in Vthe art, will deliver a constant predetermined volume-of liquid against any variable head pressure normally encountered in the operation of the machine. Since the construction and operation of pumps of this type is well known and forms no part of the present invention, the pump will not be described in detail. In accordance with the operating requirements of the pump shown, a portion thereof is mounted for swinging movement about a vertical axis 35 to vary the displacement of the pump and consequently its rate of uid delivery. To provide a convenient manually engageable -adiustment for the angular position of the pivoted portion of the pump, a hand wheel 36 is mounted exteriorly of the base I and is-provided with an interiorly threaded bore for engagement with a threaded rod 31 which is in turn pivotally connected with a link 33 pivotally connected with the movable pump portion. It should bev apparent that rotation oi the wheel 36 results in pivotal movement of the swinging pump portion and consequently a change in the rate of delivery of the pump.

Pump 30 is, in one embodiment of the invention, driven by a motor 40 conveniently mounted on a side wall of the base I0 through the shaft lil, bevel gears 42, and shaft 43. As illustrated in Figures 3 and 8 of the drawings, the shafts ill and 43 are conveniently rotatably supported in anti-friction bearings 44 mounted in apertures in webs 45 extending upwardly from the bottom wall of the base Il. Motor 46 and consequently pump 30 are normally in continuous operation during operation of the machine and the former is of sufficient power to maintain constant pump speed during each cycle of operation of the machine.

Referring now to Figures 9, and 13 of the drawings the valve 3| consists of a housing 41 having a chamber 46 therein. Port 46 provides communication between the chamber and the supply conduit 32. A port 56 provides communication between the chamber and a conduit 5| leading back to reservoir 26 and ports 53 and 54 are connected with conduits 33 and 34, respectively, leading to the cylinder 25. A valve, indicated generally at 55, is positioned within the chamber 48 and is carried for reciprocating movement therein by a valve stem 56 projecting outwardly from either end of the housing 41. For a purpose to be later described the valve is provided with a cylinder 51 in open communication with port 54 and conduit 34 and within cylinder 61 is a piston 56 connected with a yoke 53 and biased to outer position by a coil spring 66. One end of cylinder 51 is open to the atmosphere by means of a suitable port or tube 51 and the other end communicates with cylinder 41 through passage 51b. See Figure 13. When valve 56 is in its right hand position, as viewed in Figure 5, passage 61h is simultaneously in communication with port 54 and supply line 32.

Valve stem 56 has rigidly attached to it at its ends upwardly extending members 6| which in turn are rigidly pinned at their upper ends to a longitudinally slidable bar 62 mounted in projections 63 extending outwardly from the side wall of the base ||l. Bar 62 is provided with a centrally disposed integral shoulder 64 against which collars 65, slidably mounted on the bar, may abut. A member 66, pivotally connected at its upper end on the pin 61, supported on the base, is provided at its lower end with a yoke 66 positioned between the collar 65 and adapted to slide the collars along the bar 62. A coil spring 63 is positioned between collar 65 and the upper end of member 6| on either side of the bar 62. Member 66 is pivotally moved about the pin 61 by members 1| which are adjustably carried by a support 12 rigidly attached to the carriage ||,Y a partially cylindrical element 13 being provided -on member 66 for engagement by the elements As apparent from a consideration of Figure 13, the valve 3| is of the type which, when in its neutral position, will provide communication between ports 49 and 56, thus providing in eiect a by-pass for the passage of fluid to relieve any load on the fluid pump when power is not required. In addition, the valve provides for l throttling of the ow of iuid to either side of the cylinder 25 and this is accomplished by means of the conical surfaces 15 on the valve body 55 by partially closing olf the ilow of fluid to either one or the other of the conduits 34 and allowing such conical surfaces to meter the flow of fluid. A reduction in the speed of movement of the piston 24 is attained as the same approaches the end of either of its strokes and consequently the shock which would result from quickly stopping the movement of the carriage is obviated. Suitable elements, now to be described, are provided to give the required intermittent movement to the valve stem 56.

Secured to the valve stem 56 are the projecvtions 16, 11 and 16 located as shown in Figure 9, projections 16 being engageabie by a latch 66,

projections 11 being engageable by the compound latch 6| and projection 16 being'engagef.

wardly extending table 64 supported by the machine proper and by a spaced stanchion 05 and pivotally mounted on the table 04 is a ilag 06 adapted to be engaged by the leading end of stock passing through the machine. Flag 06 operates a rod 01 which, by referring to Figure 9, is connected through suitable means with the operative element of compound latch 0|. Latch 00 is operated in a manner to be later described by a slotted yoke 00 connected with the lower end 63 of the pivotally mounted member 66 by a rod 0| pivotally connected with end 6l. With the parts as described, assembled as shown in Figure 9 of the drawings, which illustrates the position the parts occupy immediately previous to the actuation of flag 06 by impingement of the stock, the operation is substantially as follows;

The stock is moving in the direction indicated by the arrow and it is obviously desired to move the carriage along with the stock upon actuation of the ilag and, therefore, the piston 24 is in its left limiting position as viewed in Figure 9. As the ilag is tripped latch -8| is released allowing left coil spring 03, which as shownl in under compression, to move valve stem 56 rapidly to the left and causing the valve member 55 to connect port 49 with port 53, and port 54 with port 50. This results in the forward movement of the carriage along with the stock and, as the carriage proceeds, left element 1| engages element 13 on arm 66 moving arm 66 in a counter-clockwise direction and causing its lower end 68 to engage right collar 65 thereby compressing right coil spring 80. This results in movement to the right of the valve stem 56 until projection 16 is engaged by latch 00 at which position of the valve stem a throttling position of the valve 55 is attained, which results in throttling of the flow ofuid under pressure to the left of piston 24 and consequently deceleration of the carriage` Latch 00 remains engaged with projection 16 until carriage reaches a predetermined position and it is then disengaged from projection 'I6 by reason of the adjustable connection 66, 58, 90, 9|. At this time right spring 69 will have become compressed and upon release of the latch 00 valve stem 56 will be moved rapidly to the right, resulting in a reversal of the ow of `fluid in conduits 33 and 34 and return of the carriage. As the carriage returns, right element 1| will engage arm 66 as the carriage approaches the end of its stroke, again compressing left spring 69 and moving valve stem 56 to the left. Valve stem 56 will move tothe left until projection18 engages the springfpressed latch 82 which position establishes another throttling position of the valve 55 to restrict the ow of uid through conduit 34 and deceleration of the re turn movement of the carriage. The carriage,

' however, will move backwards to its initial startsition, bypasses fluid from conduit 32 directly' into the return conduit The parts then will all be returned'to theirv position as shown in Figure 9 and upon subsequent actuation oi the 'nag 66 the cycle above described is repeated.

Due to the employment of a positive and uniform displacement motor as the cylinder 25 and a positive displacement pump, as described, the rate of movement of the carriage is directly proportionate to the displacement of the pump and by simply varying the displacement of the pump the rate vof movement of the carriage may be varied. The valve and its operating accoutrements, described above,'provide a satisfactory control for the system, releases the load on the motor and pump, except when work is being done, and provides an inherent method for eliminating shock due to quick reversal of movement of the carriage, thereby decreasing the vibration and jarring of the mechanism as a whole.

The invention includes improved means for operating the cutting element lduring the forward travel of the carriage and in the particular embodiment described the cutting element consists of a die set |00 (Figures 4 and 7), the one part of the die set being fixed in relation to the carriage and the other part of the die set being carried by a vertically movable cross-head III. supported and moved by a pair of vertically extending rods |02 slidably received in vertical apertures in the projection 26 of the carriage Il. In accordance with usual practice, guide pins |03 may be provided to maintain the alignment of the two parts of the cutting die set.

'I'he cross-head |04 is rigidly connected at its ends with the lower ends of the rods |02 and at its center with the rod |05 of a piston |06 vertically movable in the cylinder |01 rigidly connected with the carriage portion 26, a sliding tube |08 is rigidly connected with either end of the cylinder |01, the space Within the tubes beingl in communication with the adjacent end space of the cylinder. Tubes |08 each extend through a housing |09 provided with an elongated chamber for each of the tubes. Suitable packing means ||0 is provided between the tubes and the apertures in the end walls of the chambers to prevent the leakage of hydraulic iluid as the tubes oscillate. A series of apertures in the side walls of the tubes connect the spaces within the tubes with the spaces within the chambers.

Referring now to Figure 5, the chambers are in communication with the upper and lower ends, respectively, of a cylinder ||2 mounted adjacent the chambers and in which a piston ||3 is positioned for reciprocating movement. A rod ||4 connects the piston with a cross-head ||5 which is arranged for vertical reciprocating movement in the guide ||6 (Figure 4). Cross-head I5, and consequently piston H3, is driven by a connecting rod 8 pivotally mounted at y| I9 with the member |||5and connected at its lower` end with the throw |20 of the crank-shaft |2|. The latter is joumaled in spaced supports |22 extending upwardly from the bottom wall of base I0. Shaftl |2| is arranged to be intermittently driven by shaft 4| through gears |24'and |25, the latter being of substantial mass to provide a iiy-wheel eiTect and the single revolution clutch |26.

Inasmuch as clutches of the kind mentioned are well known in the art and no novelty is claimed herein for the clutch per se, no detailed description of the construction or operation of the clutch will be attempted. Sumce it to say that in accordance with usual practice the clutch is provided with a latch |21 (Figure 4) rotatable along with the driven shaft of the clutch and engageable by the pivoted dog |28. I'he operation of the clutch is such that upon movement oi' the dog |28 away from the latch |2`| the clutch will engage and rotate the driven shaft through one complete revolution in the direction shown, the movement being arrested by the reengagement of surface |29 of latch |21 with the dog |28. Dog |28 is connected through rod |30 and pivoted lever |3| with an operating plunger |32 biased by spring |33 to upper position whereby dog |28 will be biased to latching position.

Plunger |32 is adapted to be engaged and moved downwardly to initiate the movement of crank shaft |2| by a roller |34 carried by a frame |35 pivoted to a support |36. 'Ihe connection between members |35 and |36 allows clockwise rotation of the former relative to theV latter but limits'counter-clockwise rotation to the position shown in Figure 4. A spring i3? biases member |35 to the position shown. Member |36 is adjustably mounted on a bar |38 rigidly secured to cylinder |07 and extending in a direction parallel with the tubes |00. In operation, as the carriage is advanced along with the stock, due to operation of certain instrumentalities specically described above, a predetermined' distance, depending on the adjustment of member |36, the roller i3d will actuate plunger |32 and initiate rotation of the crank shaft iai. The cylinder lill, tubes |00, the elongated chambers in member |09 and the cylinder H3, together with all passages leading into and ut of the cylinders, having been previously completely filled with hydraulic fluid, rotation of shaft |2| with the consequent up and down movement of the piston H3 results in the down and up movement of piston |06. Consequently, each release of the dog |28 will result in a cycle of movement of the movable die of the die set |00, which cycle consists of a downward and upward stroke of the movable die member. Suflicient kinetic energy is stored in the continuously revolving gear |25 to insure the uninterrupted movement of the die through its cycle, irrespective of the shape or cross-sectional area of the stock being cut, provided the resistance encountered is not greater than that for which the machine is designed. The cycle takes place during the forward movement of the carriage and the time elapsed during the cycle is determined by the speed of rotation of shaft 4| and the ratio lof the gears |20-|25.

By reason of the employment of the crank |20 to move the die relative to the carriage, the optimum distribution of force applied to the die carrier and optimum variation in the rate of movement of the die is eiected. As shown in Figure 4, the crank when at rest is at the bottom of its path of travel and as it proceeds from its starting position its vertical component of movement gradually increases in relation to its horizontal movement, thus providing maximum force to accelerate movement of the die and connected reciprocating parts and allowing the die to substantially attain its maximum speed before the stock is encountered. 'I'he arrangement also inherently provides for gradual deceleration of the reciprocating parts which further contributes to the smoothness of operation of the machine.

Springs |40 encircling rods |02 are employed to balance the weight of the assembly |00|0|5 and therefore with the .stock in the machine the movementto the parts are proportional to the resistance encountered in cutting the stock and, this being so, the total power required during the normal operation of the machine is reduced to a minimum.

To insure the synchronous movement of piston |08 relative to piston vI I3 it is obviously required that all the spaces interconnecting cylinders |01 and ||2 by completely illled with fluid and that piston |06 be in its upper position and piston ||3 be in its lower position at the start of a cycle oi. movement. In accordance with my invention this is accomplished by providing a reservoir |4| of hydraulic fluid above the level of the cylinders and Spaces mentioned, the reservoir'being connected with the upper and lower spaces through valves |42 and |43,V respectively. l See Figure 5. A pair of cams |46 and |45 are keyed to the shaft-carrying gear |25 and suitable connecting means, as indicated schematically at I 40 and I4? in Figure 11, are provided to operate the valves |42 and |43, respectively. As the clutch |26 is actuated the cams |44 and |45 obviously move in synchronism with crank |20 and, by referring now to the diagram of Figure 1l which illustrates the condition of the parts as the dog |20 is about to be released, the operation of the synchronizing arrangement will be explained. Both valves |42 and |43 are shown in open position which, if the machine has been idle for some time, will result in the complete filling of the cylinders and spaces mentioned. Crank |20 is stopped :lust short oi dead center and, as the cycle commences at the instant the throw commences its upward movement, the high point oi cam |44 will have passed member |46 allowing valve |42 to close. Duringupward stroke of piston H3 the power is transmitted through the upper ends of the cylinders, the duid in the lower end being simply owed from one cylinder to the other. During this stroke valve |43 remains open and in case of any leakage past piston |06 the excess fluid will simply move towards reservoir |4|. As piston |23 commences its downward stroke valve |43 is closed to allow the power to -be transmitted but it will be opened again before crank |20 reaches its resting position and, if piston |06 has not already reached its upper position, the springs |40 will`move the assembly |00|06 to its upper limiting position. As crank |20 approaches its resting position cam |40 opens valve |42 to allow the spaces above the piston to be completely lled. Now, since the spaces above the pistons are completely lled with iluid and since piston H3 is in its proper starting position and piston |06 in its proper upper starting position, synchronous movement of the parts is insured during each cycle of operation.

The mechanism described above for moving the cutting die relative to the carriage is capable of being applied in mechanisms in which any type of means may be employed to recipro- `cate the carriage in synchronism with the speed of movement of the stock being acted upon. This arises from the fact that initiation of movement or energization of the die moving means is accomplished by a mechanism responsive to the position of the carriage during its forward stroke. Ink the modiiication specifically disclosed. this mechanism-consists of the clutch latch ITI-|29 operated by plungers |32 engageable by wheel |34 -rlcarried along with the carriage It is therefore possible to utilize the die moving means of the present invention in comstresses other than those required to lend the binations where means other than that disclosed is employed to oscillate carriage Such other means may consist, for example, of a rigid stop on the carriage I| for engagement by the end of the stock being cut if such'stock is of sufiicient strength and rigidity to move thecarriage, or of an arrangement utilizing an automatically operated clamp rigidly carried by the carriage and a target engageable by the leading end of the stock being cut to actuate the clamp to securely clamp the stock to the carriage during the cutting cycle of the machine. In accordance with usual practice, spring or other biasing means may be employed to return the carriage to its initial starting position.

`In addition to the ag 83 on the table B4, I provide a member |50 mounted on a vertical pivot |5| and operated by a rod |52 for the purpose of engaging cut lengths ofstock and moving the same away from the next succeeding length whereby actuation of flag 86 is not interfered with. As member |50 moves to the position shown in dotted lines in Figure 2, the cut length is kicked oi the table 84. Rod |52 is intermittently actuated by the carriage through a suitable connection, not shown.

Base IB is adjustably mounted on a plate |55, bolts |56 passing through slotted lugs |57 fastened to the base and adapted to, be threaded into suitable threaded apertures in plate |55 to clamp the base to the plate. ed to lugs |51 and engaging bolts are provided to provide precise adjustment of the lateral and angular position of the machine relative to a forming mill or other apparatus with which the machine may be used. In accordance with usual practice the plate is fixed in relation to the floor of the plant in which the machine is located.

Figure 12 illustrates a modified form of drive for the fluid pump 30 in whichbevel gears 42 are eliminated and shaft 43 replaced with a longer shaft 243 extending outwardly of the base (indicated at 2|). A pulley 244 or other connecting means is attached to the end of the shaft to which may be connected a power transmission member driven from the forming mill or other apparatus with which the cut oif machine is used or driven from a common driving -means used to drive both the cut off and the forming mill or such other apparatus. In either event the shaft 243 will rotate in synchronism with the mill or such other apparatus and for reasons advanced above, the rate of movement of the carriage will be proportional to the speed of operation of the mill or other apparatus irrespective of variations in such speed.

It should now be apparent that I have provided a machine capable of attaining the objects initially set out. The machine is capable of cutting rapidly moving stock into short lengths and by reason of the design and operating characteristics thereof this may be accomplished in a more accurate and satisfactory manner. The machine is rugged and smooth in operation requiring a minimum of maintenance and repair. The required synchronization of its moving parts is readily effected and adjusted and its power requirements are kept reasonably low.

The above specifically described embodiments. of the invention should be considered as illustrative only as obviously many changes may be made therein without departing from the spirit of scope of the invention as bounded by th appended claims. y

What I claim is: 1. In apparatus of the character described, the

Screws |58 threadcombination of a base, a carriage mounted for reciprocating movement on said base, a die mounted for reciprocating movement on said carriage, means to impart reciprocating movement to said carriage comprising a positive displacement-fluid motor, means to supply a uniform flow of fluid 'to said motor, means to vary the volume of said uniform flow of fluid, means to impart reciprocating movement to said die comprising a cylinder and piston mounted on said carriage, a cylinder and piston on said base and extendable conduits connecting said cylinders whereby movement of the last mentioned piston results in movement of the iirst mentioned piston.

2. Apparatus according to claim l further including means to operate the piston carried by the base, said means comprising a continuously rotating shaft, a second shaft, means connecting said second shaft and said last mentioned piston whereby rotation of the former results in reciprocation of the latter, and a clutch of the single revolution type interconnecting said shafts.

3. Apparatus according to claim l further including power means to operate the piston carried by the base and means responsive to the movement of said carriage in control of said power means.

4. In combination, a machine comprising a base, a carriage mounted for reciprocating movement on said base, said carriage being adapted during one stroke of its movement to move in synchronism with continuously moving stock on which the machine is to work, a working tool on said carriage, means to move said carriage comprising a power source having a normally continuously moving element, means to vary the ratio of movement between said element and said carriage, means to move said tool during movement of said carriage, and means to couple said moving element with the moving element of a driving mechanism of a production machine preceding said first named machine in a production line whereby fluctuations in the rate of stock delivery of said second mentioned machine is reflected in the rate of operation of said iirst mentioned machine.

5. In combination, a machine having a base,

a carriage mounted on said base for reciprocating movement, a tool on said carriage, means to actuate said tool during movement of said carriage, means to` move said carriage comprising a power source having a normally continuously moving element, said last mentioned means including means to vary the ratio of movement between said movable element and said carriage, means to eiect connection and disconnection between said power source and said carriage, a member engageable by the forward end of stock moving through said machine in control of said connecting means, and means coupling said moving element with a normally continuously moving element of a driving mechanism of a production machine preceding said iirst mentioned machine in the stock production line whereby the rate of movement of said carriage is synchronized with the rate of delivery of said second mentioned machine.

6. An automatic cut-ofi for shearing oil' predetermined lengths from continuously moving stock as the stock issues from a forming mill or other production machine comprising a cutter movable along with said stock and operative to sever such stock during such movement, means to move said cutter in synchronism with said stock comprising a cutter moving mechanism, means comprising the driving means of said forming mill or other production machine to drive said mechanism and means to vary the speed of said cutter independent of the speed of movement of said forming mill or other production machine driving means.

'7. Apparatus of the character described comprising a base, a tool carriage mounted for reciprocating movement'on said base, means comprising a positive displacement uid motor for moving said carriage, a tool holding slide mounted on said carriage, a cutting tool on said slide, means to move said slide comprising a cylinder and a piston mounted on said carriage, a cylinder and piston mounted on said base, extendable conduits connecting said cylinders, a hydraulic uid filling said conduits and the spaces within said cylinders not occupied by said pistons, means to drive said last mentioned piston comprising a continuously rotating shaft, a second shaft, means connecting said second shaft and said last mentioned piston whereby rotation of the former results in reciprocation of the latter, a clutch of the single revolution type interconnecting said shafts, a, variable displacement pump. for supplying uid under pressure to said motor, means to drive said continuously rotating shaft-and said pump, means to vary the displacement of said pump whereby the rate of movement of said carriage may be varied, means to drive said clutch comprising a member adjustabiy mounted on said carriage, the arrangement of the parts being such that the time interval between the starting of the carriage on its forward stroke and the starting of the movement of the slide on the carriage may be varied.

8. In apparatus of the character described, the

combination of a' base, a carriage slidably mounted on said base, a tool slide on said carriage, a cutting tool on said slide, means to move said slide on said carriage comprising a cylinder and piston on said carriage and means connecting said piston and slide, a cylinder and piston on said base, a chamber connecting with the space in said second cylinder above Said second piston,

a chamber connecting with the space in said second cylinder below said second piston. a tube rigidly connected with said carriage and in communication with the space within said rst cylinder above said first piston, said vtube extending in slidable relation through opposing side walls of said rst mentioned chamber, a second tube rigidly connected with said carriage and in communication with the space in said first cylinder below said iirst piston, said second tube extending in slidable relation through opposing side walls of said second mentioned chamber, packing means between said tubes and the walls of said chambers, apertures in said tubes within said chambers, means to maintain the spaces in said chambers, tubes and cylinders completely illled with hydraulic iiuid, and means to oscillate said second mentioned piston.

9. In apparatus of the character described, the combination of a base, a carriage mounted for reciprocating movement on said base, a slide on said carriage. means to operate said slide comprising a cylinder and piston on said carriage and means connecting said piston and said slide, a cylinder and piston on said base, an extendable conduit connecting one end of one of said cylinders with one end of the other of said cylinders, a second extendable conduit connecting the other end of one of said cylinders with the other end of the said other of said cylinders, means to reciprocate said second mentioned piston. means to keep said conduits and cylinders completely iilled with hydraulic fluid, said means being operative to insure synchronous movement between said pistons.

10. In apparatus of the character described, the combination of a reciprocating driven member. a reciprocating driving member, means to transmit the moving force of said driving member to said driven member and to synchronize the movement between said members comprising a piston and cylinder connected to each of said members, a conduit connecting the upper ends of each of said cylinders, a conduit connecting the lower ends of each of said cylinders, said driven member biasing its connected piston to upper position in its cylinder, a reservoir of hydraulic fluid positioned above said conduits andv cylinders, a conduit connecting said reservoir with said iirst mentioned conduit, a conduit connecting said reservoir with said second mentioned conduit, valves in each of said conduits connected with said reservoir and means to operate said valves in synchronism with said driving member in such manner that the iirst mentioned conduit will be in communication with said reservoir for a short interval of time as the piston connected with the driving member approaches its lowermost position and that the second mentioned conduit will be in communication with said reservoir while the piston connected with said driving member traverses its upward stroke.

11. Apparatus of the character described comprising a base. a carriage slidably mounted on said base, a metal working tool movably mounted on said carriage, means within said base to reciprocate said carriage. means within said base to move said metal working tool on said carriage, means comprising a manually engageable element accessible from outside said base to vary the speed of movement of said carriage and means to vary the time relation of movement of said tool relative to the movement oi said carriage.

12. In apparatus of the character described. the combination of a base, a carriage mounted on said base for reciprocating movement, means mounting said carriage comprising a pair oi spaced parallel hardened steel rails removably mounted on said base, an inwardly facing retaining flange on said base extending parallel with each of said rails and spaced outwardly therefrom, a plurality of bearings carried by said carriage and disposed at right angles to each other to engage the outer and inner side surfaces of said rails and other bearings carried by said carriage to engage the inner faces of said flanges.

13. In apparatus of the character described, the combination of a base, a carriage mounted for reciprocating movement on said base, a stock severing device mounted'on said carriage, means to impart reciprocating movement to' said carriage comprising a positive displacement hydraulic fluid motor, means to supply a volumetrically uniform. iiow of hydraulic uid to said motor, means to turn said supply on and off whereby movement of said carriage may be controlled,

and means to vary the volume per unit of time of said flow of hydraulic fluid whereby the rate of travel of said carriage when said supply is turned on may be varied to synchronize the movement of the carriage with the movement of the stock, and means to actuate said stock severing means during movement of said carriage.

14. In apparatus of the character described. the combination oi' a base, a carriage mounted for reciprocating movement on said base, a stock cutting means on said carriage adapted to be moved into engagement with the stock tovbe severed while said carriage moves along with said stock, means to impart reciprocating movement to said carriage in synchronism with movement oi' said stock comprising a positive displacement hydraulic uid pump, a positive displacement hydraulic iluid motor operatively connected to said carriage, controllable means to connect the outlet of said pump with said motor; and means to vary the output volume of said pump whereby the rate of travel of said carriage may be varied.

15. Apparatus according to claim 14; further includes a hydraulic iluid motor on said carriage 16. Apparatus according to claim 14 in which.

said controllable means comprises means operative in response to the advanced position of a length of said stock.

17. In apparatus of the character described, the combination of a base, a carriage mounted for reciprocating movement on said base, a stock cutting device mounted on said carriage, means to impart movement to said carriage comprising a positive displacement iiuid motor. means to supply a uniform flow of uid to said motor. means to turn said supply full on and full oil. means to vary the volume of said uniform flow of fluid, means to move said device into engagement with said stock comprising a cylinder and piston mounted on said carriage, 'a cylinder and piston on said base and conduits connecting said cylinders whereby movement of the last mentioned piston results in movement of the rst mentioned piston.

18. In apparatus of the character described, the combination of a base, a carriage mounted for reciprocating movement on said base, a slide on said carriage, means to operate said slide comprising a cylinder and piston on said carriage and means connecting said piston and said slide, a cylinder and piston on said base, a conduit connecting one end of one of said cylinders with one erid of the otherof said cylinders, a second conduit connecting the other end of one of said cylinders-with the other end of the other of said cylinders. and means comprising a single revolution clutch to reciprocate said second mentioned piston.

19. Apparatus according to claim 18 in which said last mentioned means comprising a weighted continuously rotating element, and a single revolution clutch interconnecting said element and piston wherey said piston will be reciprocated through one complete cycle upon actuation of said clutch.

20. In combination with a machine for severing predetermined lengths from longitudinally moving stock and having a carriage movable with the stock and a (cutting tool on said cartravel of the stock. and a rod engaging said member and adapted to be operated by movement of the carriage to throw the succeeding' severed lengths oi said support upon completion of the successive severing operations.

DWIGHT A. JOHNSTON. 

